Cam controlled regulating device for an injection system operating on the distributor principle



Dec. 5, 1967 F A. F. SCHMIDT 3,356,099

CAM CONTROLLED REGULATING DEVICE FOR AN INJECTION SYSTEM OPERATING ONTHE DISTRIBUTOR PRINCIPLE Filed Sept. 13, 1965 4 Sheets-Sheet l 22 I313m 5 [4- gaf iifis nvpur FROM 40 F/GZ f9a I4 ,3

r i I8 l7 /6 Inventor.

Dec. 5, 1967 A. F. SCHMIDT 3,356,099

F. CAM CONTROLLED REGULATING DEVICE FOR AN INJECTION SYSTEM OPERATING ONTHE DISTRIBUTOR PRINCIPLE Filed Sept. 15, 1965 4 Sheets-Sheet 2 10,40l/VPl/T 50b fl /PaMACC645P4raP/ F04Z) In vemor:

Fn'edr/rh Amon Franz Sch/MHZ y ATT y j Dec. 5,' 1967 Filed Sept. 13,1965 F. A. F. SCHMIDT CAM CONTROLLED REGULATING DEVICE FOR AN INJECTIONSYSTEM OPERATING ON THE DISTRIBUTOR PRINCIPLE 4 Sheets-Sheet 5 w \\Y\ 20W In renfor:

Dec. 5, 1967 F. A. F. SCHMIDT 3,356,099 CAM CONTROLLED REGULATING DEVICEFOR AN INJECTION SYSTEM OPERATING ON THE DISTRIBUTOR PRINCIPLE FiledSept. 13, 1965 4 Sheets-Sheet 4 /7 22 /8 If F/555 H 54 6/ 7 /y 38 571 5,0 5 y l f I I 2 550 m/ ur J r ra/-z/4 (yam/ifs I I J 55 53 2 4 I 5 $6 62/ ,5 do )9 39 raw/v4 2/24 SUP/ L y In wen for:

ATTY- I 3,355fi99 Patented Dec. 5, 1967 ice 3,356,099 CAM CONTROLLEDREGULATING DEVICE FOR AN INJECTION SYSTEM @PERATING ON THE DISTRIBUTORPRINCIPLE Friedrich Anton Franz Schmidt, Dr.-Seitz-Strasse, Murnau,Germany Filed Sept. 13, 1965, Ser. No. 486,743 18 Claims. (Cl. 137-26)ABSTRACT OF THE DISCLOSURE This invention relates to a regulating devicefor internal combustion engines and gas turbines, which includes adistributor injection means for feeding the fuel, by means of which anaccurate dispensing of the amount of fuel is effected for eachoperational state according to the respective requirements of theengine. This is achieved in such a manner that the influence of speedand load take effect in the regulating system independently of oneanother through a cam in the regulating system, the cam controlling therotation of an intermediate shaft for a disk mounted thereon, relativeto the rotation of the drive shaft with a disk thereon. The relativemovement of the disks creates a predetermined misalignment of diskpassageways, thereby controlling fuel flow.

This invention relates to a regulating device for an injection systemoperating on the distributor principle and intended for internalcombustion engines, gas turbines and jet engines, which includes tworotatable distributor disks provided with slots and/ or bores forfeeding fuel, a centrifugal governor for adapting the time cross sectionof the openings in the distributor disks to the speed, the disks beingarranged on one of two, or between two, distributor shafts and with thetwo rotatable distributor disks being turnable relative to one anotherby means of a cam member so that the quantity to be injected is fed inregulated manner in dependence both on speed and on a second, speedindependent factor, e.g. the position of load or the position of thethrottle valve in piston engines.

In the present invention the regulation in dependence on the position ofload or the position of the throttle valve may be effected bothexclusively or only partly with the aid of a cam member or may alsoserve only to correct the regulation by load in connection with a knownbase load regulating device. This base load regulating device may beeither a nonrotatable distributor disk relatively turnable in dependenceon load, in combination with ad ditional openings in a speed dependentrelatively turnable rotating disk, or a device for regulating the fuelpressure on the upstream side of the disks.

The regulation of the quantity to be injected takes place in dependenceon speed and load independently of one another through the intermediaryof the cam member. Regulation of the fuel pressure permits either onlyadditional influences such as e.g. the pressure and the temperature ofambient air and the temperature of the cooling water (cold start) to betaken into account for the quantity of fuel to be injected,independently of the regulation by speed and load, or also the influenceof load and the stated additional influences to be taken into account.

The above-described co-operation between a centrifugal governor of theabove-defined construction and a cam member for the application of afurther speed independent control quantity is known in principle. Thisprinciple of regulation is used in a form of construction in which forthe purpose of turning two rotatable distributor disks relative to oneanother, centrifugal weights are arranged to turn a distributor shaftwith a relatively turnable distributor disk through the intermediary ofa sleeve, an axially shiftable bushing mounted therein and finallythrough a high-pitch thread. In this known construction a cam member isarranged on an end face of the said bushing and the influence of load istaken into account on the cam member in axial direction.

In the known constructions of injection systems the given springcharacteristic of the centrifugal governor for the entire range ofregulation is not so designed that the differences of height of the cammember can be made sutliciently favorable for prescribed requirements asto regulation. In general, in a number of methods, difficulties withrespect to accuracy of regulation result from the fact that owing to thesteep regions of the cam member necessary in view of the requirements asto regulation made on the machines coming into question, great operatingand frictional forces become necessary which result in inaccuracies ofregulation.

The present invention proposes a regulating system which involvesconsiderable improvements in the mode of operation and reliability overknown regulating systems of similar type. Contrary to conventionalconstructions with one or more springs, a decisive improvement isachieved by the fact that a division of the required regulatingmovements is carried out in such a manner that part of the speeddependent regulating operations is taken into account by the springmovement by corresponding modulation of the spring characteristic.Thereby the remaining regulating movements to be actuated by the cammember become 50 small that excessive inclinations which aredisadvantageous for accuracy will be unnecessary. With the describedregulation a specific variation of the regulating characteristic, whichis adapted to the special requirements as to regulation, is carried outin dependence on speed, that is to say that not, as usual, a speeddependent progressive characteristic given by the normal springcharacteristic is produced but the regulating characteristic such asspring deflection is specially adapted to the re quirements prescribedby the shape of the cam member. As means to achieve this, combinationsknown per se of several springs are proposed, however, provision ispreferably made of individual springs the characteristic of which isrealized in the specially required manner by a variation of thethickness and the cross section as well as of the diameter of thewindings. Thus, the shape of the cam member and the springcharacteristic are systematically balanced for the individual speedranges. That is to say, the cam member is not adapted to the action of aprojected spring or group of springs, but a mutual adaptation iseffected for the purpose of obtaining an accurate adjustment of thecharacteristic curves and avoiding inaccuracies due to increasedfrictional forces.

In particular, with this combined regulating system, in the range of lownumbers of revolution and in idle motion the spring characteristic canbe so designed by appropriately shaping the spring and the cam memberthat smooth idling and uniform transitions to small positions of loadare ensured.

In order to obtain the required special regulator characteristic, usemay be made of individual springs as well as of spring assemblies. Theindividual springs may be made by various manufacturing processes whichare concerned with conventional methods for the manufacture in onepiece, e.g., preliminary forging in different thicknesses, mechanicalworking, cutting working, stepwise drawing etc. In the case ofindividual springs, also a rigid or non-positive assemblage of componentparts may be taken into consideration.

It is the object or" the present invention to make the known regulatingdevice of simpler construction and fur- .3 ther to considerably increasethe accuracy of regulation by the omission of transmission elements,particularly of the high-pitch thread. This object is achieved by movingthe cam member on a centrifugal weight in radial direction along atracer which is arranged on an intermediate shaft, is in turn movableaxially along the cam member by load rods and capable of converting thedifferences of height of the cam member into turning movement of therotatable distributor disks relative to one another.

For improving the accuracy of regulation, the stream of fuel isconducted in the same direction by incorporating a fuel feed pump ofswash plate type construction in a casing of the regulator, whereby thefuel feed is more favorable than in the previous arrangements in whichthe fuel feed pump is located outside the regulator casing, because nofuel columns tending to vibrations in the pressure pipes from the fuelfeed pump to the regulator are present in this case and, whenincorporating the fuel feed pump in the regulator casing, the fuel canflow through the regular in one direction only and need not be reversedonce or several times, as was hitherto usual. Due to this constructiondisturbance to a satisfactory flow of fuel in the pressure pipes to theinjection nozzles is largely re duced, with the result that the highprecision of the regulating device can really be fully utilized for theinternal combustion engine.

An important advantage consists in the arrangement of the rotatablerelatively turnable distributor disks relative to one another. Contraryto the hitherto known arrangements in which the two rotatable relativelyturnable disks are arranged directly side by side, these disks areseparated from one another by a fixed disk. This has the advantage thaton both sides of the two rotatable disks only relatively smallfrictional forces of the fluid are still prevailing which in the eventof a regulating turning movement can be overcome more easily by theregulating forces of the regulator than the relatively great staticfriction as occurs between the two rotatable relatively turnable disksin hitherto known arrangements. The elimination of the static frictionmeans a greater utilization of even smaller regulating forces for therelative turning movement of the disks and thus increased accuracy ofthe regulator. Furthermore, this also substantially improves thereproducibility of the dosed quantities of fuel since the hysteresis ofthe regulator is decreased.

Four embodiments of the invention will now be described by way ofexample and with reference to the accompanying drawings, in which:

FIG. 1 is a longitudinal section through a regulating device accordingto the invention;

FIG. 2 is a section taken on the line IIII of FIG. 1;

FIG. 3 is a longitudinal section through a second embodiment of theinvention;

FIG. 4 is a diagrammatic sketch illustrating the principle ofcooperation of the regulating elements;

FIG. 5 is a longitudinal section through a third embodiment of theinvention, and

FIG. 6 is a similar view of a fourth embodiment of the invention.

FIG. 1 shows an embodiment in which a distributor driving shaft 1constructed as a hollow shaft has a distributor disk 2 arranged thereon.The rotatable distributor disk 2 and a further rotatable distributordisk 4 arranged on a regulating shaft 3 are provided with passageopenings 6 and 7, respectively, for the purpose of feeding fuel in aquantitatively regulated manner. Located between the two shafts 1 and 3is a centrifugal governor 5 for turning in dependence on speed thedistributor disk 4 relative to the fuel passage openings 6 in thedistributor disk 2. Fuel under pressure can pass through a bore 8 intoan inner space 9 of the distributor and thence through a bore 10 in afixed disk 11 and the passage openings 7 and 6 in the rotatabledistributor disks 4 and 2, respectively, into outlet passages 12 andfurther through injection pipes not shown into the respective injectionnozzles.

The centrifugal governor 5 contained in the embodiment of FIG. 1includes two centrifugal weights 14 and 15 which are guided in radialdirection by rods 19. The centrifugal force is compensated by springs 20which have a speed dependent elasticity constant for the purpose ofrealizing the speed characteristic of the internal combustion engine.The centrifugal weight 14 has a cam member 13 fixed thereon and thecentrifugal weight 15 carries a counterweight 21. A curved boundarysurface 40 (FIG. 2) of the cam member 13 can be traced by a feelerroller 18 provided wit-h a restoring spring, not shown, of a tracer 17which is mounted on an intermediate shaft 16, and this tracing movementwill be converted into turning movement of the intermediate shaft 16relative to the driving shaft 1. As the tracer 17 is guided in alongitudinal slot 22 in the regulating shaft 3, turning of theintermediate shaft 16 relative to the driving shaft 1 is at the sametime transmitted to the regulating shaft 3. The intermediate shaft 16 ismounted within the regulating shaft 3 so as to be axially shiftable independence on load. The feeler roller 18 can trace the cam member 13 inradial direction in dependence on speed and in axial direction independence on load. The centrifugal weights are guided symmetrically tothe regulating shaft 3 by cranks 38 through the intermediary of acoupling member 39.

The rods 19 are intended to guide the movement of the centrifugalweights in parallel. The cranks 38 together with the disks 39 areintended to ensure an identical deflection by coupling the twocentrifugal weights. The mode of operation is easily understood whenFIGS. 1 and 2 are compared taking into consideration the followingexplanation. Each of the centrifugal weights 14 and 15 is provided withtwo bores, the centrifugal weight 14 having the bores 19a and thecentrifugal weight 15 the bores 19b. These bores 19a and 1% are arrangedin such a manner that the centrifugal weights 14 and 15 are movable onthe rods 19 along the bores, which rods are mounted in the shaft 1, andthe centrifugal weights are guided by the rods 19.

On one end face of the centrifugal weights 14 and 15 (the right-handside of FIG. 1) each centrifugal weight is provided with a rotatablecrank 38.

These cranks are connected through the intermediary of a coupling member39 designed as a disk. In this manner the centrifugal weights 14 and 15are kinematically connected through the intermediary of the cranks 38and the coupling member 39 in such a manner that the deflection of thecentrifugal weights is always identical. Due to this construction therespective characteristic curves can be realized with utmost accuracy inthe entire working range of the machine by the combined design of thespring characteristic on the one hand and of the cam member on the otherhand. In particular, with this combined regulating system, in the rangeof small numbers of revolution and in idle motion the springcharacteristic will be so designed by correspondingly shaping the springand the cam member that great paths of the regulating members willresult at small regulating forces so that smooth idling and uniformtransitions to small load points are ensured.

The embodiment shown in FIG. 3 includes a centrifugal governor 45 havingtwo centrifugal weights 43 and 44 which are pivotable about pins 23 and24, respectively, and guided in radial direction in guideways 42. Thecentrifugal force is compensated by a restoring spring 46- arranged on adriving shaft 41, which spring may also have a speed dependentelasticity constant. The centrifugal weight 43 has a cam member 47 fixedthereon and the centrifugal weight 44 carries a counterweight 48corresponding to the cam member 47. Also in this embodiment a curvedboundary surface of the cam member 47 can be traced by a feeler roller50 provided with a restoring torsion spring 25, of a tracer 51 which isfixed on an intermediate shaft 52, and this tracing movement will beconverted into turning movement of the intermediate.

shaft 52 relative to the driving shaft 41. An actuating rod 26 is fixedon the intermediate shaft 52 for the purpose of applying load fromoutside onto the intermediate shaft 52 and transmitting turning movementof the intermediate shaft 52 relative to the driving shaft 41 from theintermediate shaft to a regulating shaft 53. This actuating rod 26 isaxially guided in an axial slot 49 of the regulating shaft 53 andmovable by means of actuating rods 27 and 23, a ring 29 and a bearing 30from load rods arranged to turn the ring 29. The actuating rods 27 and28 are slidable in slanting grooves 31 and 32 of the ring 29longitudinally of the axis of the regulating shaft 53.

That portion of the device containing the elements 26 and 29 serves fortransforming the rotating movement initiated by an accelerator pedalthrough the toothed rim 29a into a longitudinal movement of the shaft 52for the purpose of moving the tracer 51. In this connection thefollowing detailed explanations are made:

The ring 29 is rotated from the accelerator pedal rods. This is carriedout through a toothed rack (not illustrated) actuated by the acceleratorpedal rods, the rack engaging the toothed rim 29a of the ring 29. Aslanting groove 32 is arranged within the ring 29, the rods 27 and 28sliding in this groove and axially moving in the longitudinal grooves 31and 32 when the ring 29 is rotated. The rods 27 and 2.8 engage the bores30a and 30b in the outer ring of a needle bearing 30 which is alsoaxially movable. When rotating the ring 29 the rod 26 is thus axiallydisplaced and also axially displaces the shaft 52 and the tracer 51. Abiasing means for measuring the load is neither provided nor necessarybecause the movement of the load lever is positively transmitted throughthe intermediary of the described mechanism to the tracer. The spring 25is merely intended for pressing the tracer 51 against the cam member 47in order to maintain the positive connection between the tracer 51 andthe cam member 47. A rigid coupling between the intermediate shaft 52 orthe regulating shaft 53 and the driving shaft 41 by the actuating rod 26is avoided by appropriate openings 33 and 34 in the driving shaft 41.

The quantity of fuel to be injected can be regulated in dependence onspeed and load by the relative turning movement of the rotatabledistributor disks 2 and 4 according to the above-described principle andadditionally in dependence on other factors (e.g. pressure andtemperature of ambiency, temperature of cooling water) in conjunctionwith a variation of the injection pressure. Generation of pressure iseffected e.g. by means of a pressure regulator 37 which can beinfluenced by the third factor.

FIG. 4 shows a diagrammatic sketch illustrating the co-operation of theregulating elements. The centrifugal weights 14 and 15 exert acentrifugal force on the springs 20. The centrifugal weights are movedapart according to the specially designed spring characteristic independence on speed. This movement is transmitted to the cam member 13in the direction of arrow 35. In accordance with the differences ofheight of the construction of the cam member in this direction ofmovement, this movement is transferred to the tracer 17 which isconnected to the output of the regulator. The speed independent controlquantity in the direction of arrow 36 is transmitted from the tracer 17to the cam member 13, with the tracer 17 moving over the cam member 13perpendicularly to the speed dependent direction of movement indicatedby arrow 67, and an additional movement of the regulating elements atthe output of the regulator is achieved by corresponding differences ofheight of the construction of the cam member 13 in this direction. It isof no consequence to the principle of regulation whether the speeddependent movement is transmitted from the centrifugal weights primarilyto the cam member 13 and from this secondarily to the tracer 17 or viceversa. The

same applies analogously to the application of the speed independentcontrol quantity.

FIG. 5 shows an embodiment of the regulating system in which the cammember 13 is fixed on the centrifugal weight 14 of the centrifugalgovernor and movable by the centrifugal weight 14 in radial directionindicated by arrow 69 along the tracer 17 which is arranged on theintermediate shaft 16 and movable axially along the cam member 13 by thespeed independent control quantity 68, the differences of height of theconstruction of the cam member 12 being transmittable as turningmovement to the output shaft 3 of the regulator.

The embodiment shown in FIG. 6 corresponds practically to the embodimentof FIG. 1 having a fuel feed pump incorporated therein. Fuel can passunder small inlet pressure through a bore 55 into an inner space 56 of afuel feed pump 54 known per se. The distributor driving shaft 1 has aswash plate 57 fixed thereon which is driven with the speed of theregulator. A piston 58 is constantly urged by a pressure spring 59against an oblique surface 60 of the swash plate 57 so that it canerform reciprocating movements within a bore 61 during the rotation ofthe swash plate 57. In the moved-out position of the piston 58 a suctionvalve 63 is opened by a bore 62 of the piston and fuel sucked into thebore 61. When the piston 58 is moved into the bore 61, the suction valve63 will be closed and the fuel fed into an inner space 65 of thedistributor on opening of a pressure valve 64. From the inner space 65the fuel passes through the passage opening 6 inthe-rotating distributordisk 2, through the bore 10 in the fixed disk 11 and through the passageopening 7 in the second rotating distributor disk 4- into outletpassages 66 and further through the injection pipe to the respectiveinjection n02.- Zles.

If this effective control cross section or open passage cross section ofthe two rotating disks would remain constant at increasing speed of thedisks the amount of fuel passing through the set of disks per revolutionwould continuously decrease with increasing speed because the period oftime in which the effective (open) control cross section of the rotatingdisks passes over the input and output bores in the fixed disks wouldbecome smaller and smaller.

The-time cross section means the integration of these passage crosssections over the time differentials.

In order that the penetrating amount of fuel does not decrease, ordecreases more or less according to the requirements when the speedincreases according to the operational requirements of the respectiveengine (e.g. an Otto engine), a centrifugal governor causes a relativerotation of the two rotating disks whereby the effective control crosssection can be enlarged in order to be capable of adjusting the timecross section to the requirements by changing the flow cross section ofthe fuel passage.

In the case of decrease of speed the same applies analogously.

The invention may be embodied in other specific forms without departingfrom the spirit or essential characteristics thereof. The presentembodiments are therefore to be conidered in all respects asillustrative and not restrictive, the-scope of the invention beingindicated by the appended claims rather than by the foregoingdescription and all changes which come within the meaning and range ofequivalency of the claims are therefore intended to be embraced therein.

I claim:

1. A fuel regulating device comprising a distributor injection meanshaving fuel passage means t'herethrough, a centrifugal governorassociated with an input shaft, a cam member movable radially of saidinput shaft by said centrifugal governor, a cam tracer carried by anintermediate shaft, and first and second means for varying the crosssection of said passage means in speed dependent and speed independentrelation respectively, relative to said input shaft, said first meanscomprising at least one spring having a pre-selected deflectioncharacteristic and cooperating with said governor for relative movementof said cam member and cam tracer; said second means including meansresponsive to an external load being associated with said intermediateshaft for movement of said cam tracer relative to said cam member.

2. A regulating device as claimed in claim 1, wherein the springcharacteristic is designed to correspond to the path of movement ofgovernor weights such that in ranges of regulation in which relative-1ygreat paths of a contact element of the tracer on the cam member must beachieved, thus normally steep regions of the cam member would benecessary, the movement of centrifugal weights forming the centrifugalgovernor will be large, but in ranges where only small regulatingmovements are required, the movements of the centrifugal weights will besmall.

3. A regulating device as claimed in claim 1, wherein the cam member isdirectly carried by a centrifugal weight of the centrifugal governor.

4. A regulating device as claimed in claim 1, wherein the centrifugalgovernor has two centrifugal weights, a casing portion of the inputshaft carries the centrifugal governor, means are provided for guidingthe two centrifugal weights of the centrifugal governor radially to theaxis of the regulator in the casing thereof, two cranks serve to guidethe two centrifugal weights of the centrifugal governor symmetrically tothe axis of the regulator in the casing thereof, each spring having aspeed dependent elastically constant and wherein said springs areradially acting.

5. A regulating device as claimed in claim 4, wherein the means forguiding the centrifugal weights radially to the axis of the regulatorcomprise rods.

6. A regulating device as claimed in claim 4, wherein the means forguiding the centrifugal weights symmetric to the axis of the regulatorcomprise connecting links.

7. A regulating device as claimed in claim 2, wherein the springcharacteristic is designed by variable thickness of the windings independence on speed in such a manner that the required variation inlength of the spring is realized in such a way that the associatedangles of inclination on the cam member are reduced to mean values on anaverage.

8. A regulating device as claimed in claim 2, wherein the springcharacteristic is designed by variation of the diameter of the windingsin dependence on speed in such a manner that the required variation inlength of the spring is realized in such a way that the associatedangles of inclination on the cam member are reduced to mean values on anaverage.

9. A regulating device as claimed in claim 2, wherein the springcharacterstic is designed by variation of the pitch in dependence onspeed in such a manner that the required variation in length of thespring is realized in such a way that the associated angles ofinclination on the cam member are reduced to mean values on an average.

10. A regulating device as claimed in claim 2, wherein by combining atleast two of the following three measures: variable thickness of thewindings, variation of the diameter of the windings and variation of thepitch the spring characteristic is designed in dependence on speed insuch a manner that the required variation in length of the spring isrealized in such a way that the associated angles of 8 inclination onthe cam member are reduced to mean values on an average.

11. A regulating device as claimed in claim 1, wherein when the deviceis used for internal combustion engines and gas turbines, springcharacteristic and cam member are designed to co-operate in such amanner that in the range of small outputs and in idle motion very smallangles of inclination of the cam member are associated with large pathsof centrifugal weights forming the centrifugal governor, thereby toachieve particularly smooth idling and good transitions in the range ofsmall positions of load.

12. A regulating device as claimed in claim 2, wherein relativelyrotatable distributor disks comprise said passage means, said inputshaft carrying one said disk, and a distributor shaft carrying anotherdisk, said distributor shaft being non-positively connected to theintermediate shaft tracer and the tracer itself is capable ofconverting, by its non-positive connection with the distributor shaft,the differences of height of the cam member directly into turningmovement of the rotatable distributor disks relative to one another.

13. A regulating device as claimed in claim 1, wherein the centrifugalgovernor has two centrifugal weights, a casing portion of the inputshaft rotatably mounts the centrifugal governor, connecting links areprovided for radially guiding the two centrifugal weights of thecentrifugal governor, and axially acting regulator spring means having aspeed dependent elasticity constant are provided for restoring the twocentrifugal weights.

14. A regulating device as claimed in claim 1, wherein a fuel feed pumpis provided associated with said distributor injection means.

15. A regulating device as claimed in claim 14, wherein the fuel feedpump is of swash plate type construction with axial passage of fuel tothe distributor disks.

16. A regulating device as claimed in claim 1, wherein a pressureregulating element is provided for additionally regulating the fuelpressure and relative turning of the rotatable distributor disks iseffected by speed and load in combination with a known regulation of thequantity of fuel in dependence on an additional factor by the additionalregulation of the fuel pressure by means of the pressure regulatingelement.

17. A regulating device as claimed in claim 1, wherein the combinedspeed dependent and speed independent variation of said passage means ofthe distributor injection means serving to supply the fuel is effectedby relative rotation of two rotating distributor disks provided withslots.

18. The regulating device of claim 17 wherein said passage means definesa time cross-section of fuel flow during operation of the device.

References Cited UNITED STATES PATENTS 1,096,386 5/1914 Norton 73-5372,081,466 5/1937 Tarisien 137-56 2,352,736 7/1944 Richmond 137--292,805,549 9/1957 Hensleigh et al. 6054 2,867,084 l/l959 Criswell 6039.283,016,911 1/1962 Strand l37----33 3,200,886 8/1965 Magri et a1. 60-39.28X

JULIUS E. WEST, Primary Examiner.

1. A FUEL REGULATING DEVICE COMPRISING A DISTRIBUTOR INJECTION MEANSHAVING FUEL PASSAGE MEANS THERETHROUGH, A CENTRIFUGAL GOVERNORASSOCIATED WITH AN INPUT SHAFT, A CAM MEMBER MOVABLE RADIALLY OF SAIDINPUT SHAFT BY SAID CENTRIFUGAL GOVERNOR, A CAM TRACER CARRIED BY ANINTERMEDIATE SHAFT, AND FIRST AND SECOND MEANS FOR VARYING THE CROSSSECTION OF SAID PASSAGE MEANS IN SPEED DEPENDENT AND SPEED INDEPENDENTRELATION RESPECTIVELY, RELATIVE TO SAID INPUT SHAFT, SAID FIRST MEANSCOMPRISING AT LEAST ONE